Force-feed lubricating device



Filed Sept. 22, 1927 Patented Apr. 1, 1930' I I q UNITED STATES PATENT OFFICE IRVING COWLES, OF CHICAGO, ILLINOIS, ASSIGNOR TO UNION BANK OF CHICAGO, TRUSTEE, OF CHICAGO, ILLINOIS, A CORPORATION OF ILLINOIS FORCE-FEED LUBRIGATING DEVICE Application filed September 22, 1927. Serial No. 221,198.

This invention relates to force-feed lubrimaximum requirements of the respective cation of bearings by means of a source of inbearings per time unit. Economic manufactermittent high and low pressures associated ture of metering devices requires thatthe with metering devices mounted on the bearnumber of sizes of the latter be limited and,

ings for delivering a substantially accurately consequently, an ideal degree of accuracy in 55 measured volume of lubricant to each of sevoil distribution is quite as impossible as it is eral bearings at each high pressure interval unnecessary. To permit a reasonably close and thereupon shutting off flow to said bearapproach to the ideal accuracy without deings. feating cost economy in manufacture rem The present invention relates particularly quires, therefore, acertain rangeof adjust- 50 to a specific improvement in the meteringdement of the individual metering devices and vices at the bearings and has for its object to the particular object of the present invention v provide devices of this character equipped is to provide very simple and eflicient adjustwith means for permitting easy adjustment ing means whereby each of a series of meterthereof for varying the volume of lubricant ing devices may be adjusted so that the mini- 5 delivered therefrom at each operation thereof mum volume delivered by a larger size may in response to high pressure in the oil line in be substantially equal to the maximum volwhich the device is interposed. v ume capable of being delivered by the next In machines or mechanisms provided with smaller size while, vice versa, the maximum bearings requiring lubrication, there are usuvolume capable of being delivered is substan- 7o ally bearings of many different diameters tially equal to the minimum'of the next larger and lengths while the shafts or other rotatsize. able elements journalled therein rotate at dif- The preferred embodiments of the invenferent speeds respectively and under widely tion are illustrated in the accompanying.

Varying loads. These several bearings re drawings, wherein: quire volumes of lubricant, respectively, dif- Figure 1 is a sectional view, partly in elevafering quite as widely as the dimensions of tion, of bearings equipped with metering deand other conditions pertaining to the same vices; and fittings for associating the same so that while, theoretically, it appears possiwith a source of lubricant, constructed in acble to determine the volume of lubricant per cordance with the invention. 7

time unit required for each thereof, practice Figure 2 is a sectional view on the line 22 has demonstrated that this is not so because of Figure 1 on an enlarged scale.

of variations in play or tolerance in the Vari- Figure 3 is a sectional View similar to Figous bearings and consequent leakages. -ure 2 showing another or modified embodi- In equipping a machine or mechanism with ment of the invention. 5

a force-feed lubricating system, the propor- Figure 4 is a perspective viewof the piston tionate 7 requirements of each of the several or plunger element of the metering devices of bearings may be estimated and each bearing Figs. 1, 2 and 3.

equipped with a metering device capable of Figure 5 is a sectional perspective view of 40 supplying its maximum requirements. F eedthe adjusting sleeve employed. 90 ing to each bearing the maximum require- The subject-matter of the present invenment thereof will, in most instances, result tion, which relates to the metering devices in waste and in inadequate supply, respecand fittings, per. se, is intended and adapted tively, depending upon unknown conditions for use in connection with a pump or simiexisting in the several bearings. lar source of lubricant under alternate high 96 Hence, in applying a force-feed lubricating and low pressure, examples of pumps adaptsystem to a machine or mechanism, the ened for the purpose being disclosed in my cogineer or mechanic must be governed by the pending applications, Serial Nos. 98,886,

area of bearing surface and speed of rota- 131,843 and 187,741, filed, respectively March tion as a basis for determining the probable 31, 1926; August 27, 1926 and April 30, 1927,

the last-mentioned application also showing but not claiming metering devices of the same type as are illustrated in the instant case but devoid of adjusting means. Each of the metering devices, per se, comprises a casing 1, preferably provided with a hexagonal exterior surface 2 between its ends and which is internally longitudinally bored to provide an axial cylindrical chamber 3 extending from one end of the casing 1 to a point between its ends where it terminates in an annular shoulder or valve seat 4 and connects with a smaller bore 5. The latter, as shown in Figure 2, terminates at its other end in an annular shoulder 6 and connects with still smaller diameter discharge bore 7.

Bordering the outer end of the bore 7 is a valve seat 8 on which the spring-held checkvalve/9 seats, the latter being disposed in the go bore 10 at the discharge end of the casing 1.

Forced into and frictionally held in place in the bore 10 is an annularly flanged washer 11 u on which the compression spring 12 which olds the valve 9 normally seated, is

u su ported.

ciprocable within the chamber 3 is the iston element 13 the stem 14 of which proects into the bore 5, said piston element being of sufficiently smaller diameter than the chamber 3 to permit somewhat resisted and restricted flow of lubricant past said piston. A relatively long helical compression spring 15 supported upon the shoulder 6 and bearing upon piston element 13, serves to hold the latter normally disposed at the mouth or intake end of chamber 3.- A washer 16 of a suitable flexible material covers the annular shoulder of the piston-element against which the spring 15 bears,'said spring serving to 40 hold said washer in lace.

The seat surface 0 the check valve 9 is also covered with a similar flexible washer which is held in place by means of the pin 17 driven intoa central openin in said valve.

In the structure of ig. 3 the bore 5 terminates at the inverted shoulder or valve-seat .8 for the check-valve 9, the shoulder 6 and bore 7 being omitted. In this structure the vspring 15 is supported upon the check-valve (F-*9, the proportionate strength of springs 12 and 15 being such that when the latter is under its maximum compression as determined by the seating of the washer 16 on the seat 4, the check-valve 9 will be maintained on its 5 seat and will be unseated only in response to fluid pressure within the casing sufficient to overcome the balance of resistanceoflered by the spring 12. it

The operation of both types of metering devices above described is identical, the introduction of oil under pressure to the casing 1 causing the iston element'13 to move toward its seat, the y-pass space around said piston causin fluid below the same to be almost 66 instan y under the samepressure as the inflowing fluid, the pressure of the latter being far in excess of what is necessary to overcome the resistance of the spring 12. Thus the incoming fluid, in the absence of resistance to discharge beyond the check-valve. 9 by the presence of fluid trapped between the check-valve and the bearing surface by reason of a very tight or frozen bearing, will force the piston element to the seat st and shut ott' further flow. At substantially this moment, the cheek-valve 9 also seats and thus traps fluid between it and the seat -.lso that upon relief of pressure at the intake end of the casing 1, the piston element will be restored to its normal position by the spring 15 and, by reason of the fact that the last-mentioned trapped fluid cannot escape, the fluid in the chamber 3 will transfer around thepiston 13 to be disposed between the latter and the check-valve 9. Here it will remain until a further forced flow into chamber 3 takes place I degree such as will create baclcpressure below the check-valve 9 suflicient'to slow up flow past the latter, then the movement of the piston 13 will be eitherretarded or arrested and a continuous slow flow of lubricant into the hearing will continue so long "as the pressure on the incoming lubricant is maintained by the pump or the like employed to effect forced flow. But upon relief of said pressure the result will be identical with that occurring at a normal hearing.

The casings 1 and chambers 3 may be varied either in length or diameter or both to thereby vary the volume of lubricant discharged at each pressure operation. Thus very small bearings may be supplied each with only a very minute volume of oil while larger bearings may be fed with one or more cubic centimeters of lubricant simultaneously, andfrom the same source, the tight or frozen bearings only being supplied with a non-measured volume of lubricant.

In order that the measured volume of lubricant fed by each device independently, of all others may be varied without substituting a larger or smaller device therefor, I

provide a Very simple and eflicient adjusting means which, preferably, is incorporated in the pipe fitting by means of which thecasing 1 is connected with the piping leading from the pump or other source to the several bearings to be lubricated. These fittings consist of the usual line known as couplings, Ts, elbows, etc., and differ from the ordinary pipe fittings only in that those shown are equipped with compression pipe couplings for connecting the same with copper tubing.

Thus, as shown in Fig. 1, the T-coupling 18 is provided at the ends of two of its arms with compression pipe couplings 19 by means of which it is detachably connected with tubing 20 leading from the pump or the like to said fitting 19 and with the tubing 21 leading to another fitting or fittings. The third arm off'said fitting 18 is provided with a stepped bore, the outer portion 22 of which is of larger j diameter than the inner portion 23 and being threaded to fit the outer or intake threaded end portion of, the casing 1, this thread being a tapered or pipe-thread. The thread of the inner portion 23 of said bore is cylindrical and receives, the threaded sleeve 24 which is of smaller external diameter than the diameter of thejchamber 3 of casing 1 so that it may project into the same. The outer or visible end of said sleeve 24 is slotted to receive a screw-driver and is preferably fitted snugly to the threads of' bore 23 so that it will retain any position to which it is adjusted. The bore of said sleeve 24 is also stepped to provide a shoulder 25 between its ends on which a strainer 26 of small mesh is supported, the same being held in place by the annularly flanged washer 27 driven into the larger diameter portion of said bore.

This construction is very advantageous in that the pipe fitting can be finished on an ordinary chucking machine at no greater cost than the conventional type and the sleeves are cheaply produced by ordinary automatic screw machines and are easily and cheaply assembled.

In practice the spring 12 for the check valve 9 is of such strength as to practically equal a counter pressure of twenty-five lbs. per sq.'in. while the spring 15 affords a maximum resistance equaling a pressure of about fifteen lbs. per sq. in. on the piston. The lubricant is preferably introduced at a pressure not less than one hundred and preferably approximating from two to four hundred pounds per square inch. These working pressures have been found to be very dc sirable though the system will operate efficiently under a pressure of fifty pounds per square inch as an approximate minimum under the aforesaid spring resistance conditions. These conditions may, of course, be varied.

The casings 1 are designed for low cost of production by automatic screw machines so that the total cost of installation of the system per bearing is very small.

The tolerance or free annular space around the piston is, ordinarily about .004 inch and practice has demonstrated that this permits the use of either light or heavy oil without appreciable difierence in the accuracy of the volume discharged at each operation. This is very advantageous in the case of automotive vehicles andmachinery which is operated in the open in cold weather as it permits changing from heavy to light oil and vice versaand insures substantially the same degree of efficiency in the lubrication of warm and cold bearings so long as the oil used is not congealed to a substantially non-fluent state.

I claim as my invention:

1. A-lubricant measuring device of the type defined comprising a casing equipped with a reciprocable spring-held fluid pressure responsive valve element adapted to shut off flow through said casing following discharge of a substantially measured volume of lubricant therefrom, a pipe fitting connecting said casing with lubricant supply piping and a threaded sleeve in said fitting adjustable axially of said casing and affording a stop against which said valve element is normally held by said spring, said adjustable member determining the operative stroke of said valve-element.

2. A lubricant measuring device of the type describedincluding a casing having a cylindrical chamber open at one end and equipped at its other end with a valve-seat, a spring-held reciprocable valve element in said chamber normally disposed at the open end thereof, a pipe fitting constituting a cap for said open end and connecting said casing with lubricant supply piping, and a threaded sleeve in said fitting constituting an adjustable stop for said valve element for determining its operative stroke.

3. A lubricant measuring device of the type specified comprising a casing having a cylindrical chamber open at one end and terminating at its other end in a valve-seat, a discharge port at the other end of said casing, a check-valve controlling the same a spring for maintaining said check-valve normally seated, an annularly flanged washer driven into the discharge end of said casing and supporting said spring, a reciprocable piston valve disposed in said chamber, a passage connecting the latter with said discharge port, a spring in said passage engaged with said piston valve for normally maintaining the latter off the first-named valve seat, said last-named spring being appreciably weaker than the check-valve spring and overcome by the latter, and a pipe fitting connecting the casing at the open end of said chamber with lubricant supply piping.

4. A lubricant measuring device of the type specified comprising a casing having a cylindrical chamber open at one end and terminating at its other end in a valveseat, a discharge port at the other end of said casing, a checkvalve controlling the same, a spring for maintaining said check-valve normally seated, an

annularly flange washer driven into the discharge end of said casing and supporting said spring a reciprocable piston valve disposed in said chamber, a passage connecting the lat- 5 ter with said discharge port, a spring in said passage engaged with said piston valve for normally maintaining the latter oft the firstnamed valve seat, said last-named spring being appreciably weaker than the check-valve n spring and overcomeby the latter, and supported upon said check-valve.

5. A lubricant measuring device of the type specified comprising a casing having a cylindrical chamber open at one end and terminating at its other end in a valve-seat, a discharge port at the other end of said casing, a spring-held check-valve normally sealing said port, a passage connecting the latter with said discharge port, a spring in said passage engaged with said piston valve for normally maintaining the latter off the first-named valve-seat, said last-named spring being appreciably weaker than the check-valve sprin and overcome by the latter and supporte upon said check-valve.

IRVING COWLES. 

